U.S. patent number 9,334,946 [Application Number 14/063,650] was granted by the patent office on 2016-05-10 for vehicle transmission pressure regulator valve.
This patent grant is currently assigned to SUPERIOR TRANSMISSION PARTS, INC.. The grantee listed for this patent is Superior Transmission Parts, Inc.. Invention is credited to Dean Mason.
United States Patent |
9,334,946 |
Mason |
May 10, 2016 |
Vehicle transmission pressure regulator valve
Abstract
A vehicle transmission pressure regulator valve for regulating
oil flow to a torque converter clutch from a pump in a lubrication
circuit of the transmission wherein the valve includes a plurality
of spaced annular lands integrally formed with a core body of the
valve and wherein at least an outermost regulation line dump
circuit control land and a second intermediate torque converter
feed control land are tapered inwardly toward the core body and in
a direction of an innermost pressure regulator balance land so to
dynamically regulate flow into the regulation dump line and the
torque converter circuit feed circuits due to the tapered surfaces
of the two valve lands and wherein an additional converter assist
spring is seated within an inner end of the valve so as provide a
continuous force urging the valve toward and open position within
the valve seat bore of the transmission.
Inventors: |
Mason; Dean (Tallahassee,
FL) |
Applicant: |
Name |
City |
State |
Country |
Type |
Superior Transmission Parts, Inc. |
Tallahassee |
FL |
US |
|
|
Assignee: |
SUPERIOR TRANSMISSION PARTS,
INC. (Tallahassee, FL)
|
Family
ID: |
55859912 |
Appl.
No.: |
14/063,650 |
Filed: |
October 25, 2013 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
|
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61718316 |
Oct 25, 2012 |
|
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Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F16K
11/0716 (20130101); F16H 61/029 (20130101); F16K
11/0708 (20130101); F16H 57/0435 (20130101); F16K
3/00 (20130101); F16H 2061/0279 (20130101); Y10T
137/2663 (20150401) |
Current International
Class: |
G05D
11/00 (20060101); F16H 57/04 (20100101) |
Field of
Search: |
;137/115.13,115.14,115.26,118.06,118.07 ;60/329 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Arundale; R. K.
Attorney, Agent or Firm: Dowell & Dowell, PC
Claims
I claim:
1. A pressure regulator valve for use in an automatic transmission
and wherein the valve is configured to be seated within a bore of a
transmission so as to control fluid flow from a transmission pump
to a torque converter, pressure regulator balance flow and flow to
a pressure regulator dump circuit, the pressure regulator valve
comprising a body including spaced first and second core portions
from which first, second and third fluid flow controlling annular
lands extend, the first land being formed at an inner end of the
body for controlling pressure regulator balance fluid flow, the
second land being spaced between the first and third lands for
controlling fluid flow to a torque converter of a transmission, the
second land having a rear continuously inwardly tapering conical
surface that extends toward and terminates at an outer wall of the
first core portion between the first and second lands, the third
land being spaced from the second land for controlling fluid flow
to a pressure regulator dump circuit, the third land having a rear
inwardly tapering conical surface that terminates at an outer wall
of the second core portion extending between the second and third
lands, and a boost sleeve and spring supporting extension portion
extending forward of the third land whereby the tapering surfaces
of the second and third lands allow a variable flow rate to be
established relative to the fluid flows being controlled thereby,
and a blind hole extending from the inner end of the valve body
through the first land and into the first core portion, and a
balance assist spring mounted partially within the blind hole for
providing force to continuously urge the pressure regulator valve
against pressure regulating springs mounted about the extension
portion of the valve when the pressure regulating springs are
mounted within the boost sleeve surrounding the extension
portion.
2. The pressure regulator valve of claim 1 including a hole
provided through the first core portion and transverse to a central
axis of the body of the pressure regulator valve.
3. The pressure regulator valve of claim 1 wherein the second land
is formed so as to provide a clearance between the second land and
the bore in which the valve will be mounted so as to allow fluid
flow to pass between the second land and walls defining the
bore.
4. The pressure regulator valve of claim 1 wherein the rear
inwardly tapering conical surfaces of the second and third lands
are angled between 20.degree. to 50.degree. relative to a central
axis of the body.
5. The pressure regulator valve of claim 1 wherein the rear
inwardly tapering conical surfaces of the second and third lands
are angled between 35.degree. to 45.degree..
6. The pressure regulator valve of claim 5 wherein front faces of
the first and second lands taper inwardly toward the first and
second core portions, respectively.
7. The pressure regulator valve of claim 6 wherein the front faces
taper at approximately 45.degree. relative to the central axis of
the body.
8. The pressure regulator valve of claim 5 wherein the first land
has generally planar front and rear surfaces.
9. The pressure regulator of claim 1 wherein the first land has
generally planar front and rear walls.
10. A pressure regulator valve for use in an automatic transmission
and wherein the valve is configured to be seated within a bore of a
transmission so as to control fluid flow from a transmission pump
to a torque converter, pressure regulator balance flow and flow to
a pressure regulator dump circuit, the valve comprising a body
including spaced first and second core portions from which first,
second and third flow controlling annular lands extend, the first
land being formed at an inner end of the body for controlling
pressure regulator balance flow, the second land being spaced
between the first and third land for controlling flow to a torque
converter of a transmission, the second land having a rear inwardly
tapering conical surface that terminates at an outer wall of the
first core portion between the first and second lands, the third
land being spaced from the second land for controlling fluid flow
to a pressure regulator dump circuit, the third land having a rear
inwardly tapering conical surface that terminates at an outer wall
of the second core portion, and a boost sleeve and spring
supporting extension extending forward of the third land whereby
the tapering surfaces of the second and third lands allow a
variable flow rate to be established relative to the fluid flows
being controlled thereby and a blind hole extending from the inner
end of the valve body and into at least a portion of the valve
body, and a balance assist spring mounted at least partially within
the blind hole for providing force to continuously urge the
pressure regulator valve against pressure regulating springs
mounted about the extension of the valve when the pressure
regulating springs are mounted within the boost sleeve surrounding
the extension portion.
11. The pressure regulator valve of claim 10 wherein the second
land is formed so as to provide a clearance between the second land
and the bore in which the valve will be mounted so as allow fluid
flow to pass between the second land and walls defining the
bore.
12. The pressure regulator valve of claim 10 wherein the rear
inwardly tapering conical surfaces of the second and third lands
are angled between 20.degree. to 50.degree. relative to a center
axis of the body.
13. The pressure regulator valve of claim 10 wherein the rear
inwardly tapering conical surfaces of the second and third lands
are angled between 35.degree. to 45.degree..
Description
BACKGROUND OF THE INVENTION
1. Field of the Invention
The present invention is directed to automotive vehicle
transmissions and more particular to pressure regulating valves for
controlling oil flow through hydraulic circuits from an oil pump to
both a torque converter and a lubrication/relief valve and to a
pressure regulator balance port and to a method of modifying valve
lands to provide for increased fluid supply to the torque converter
and to establish a steady stream progressive flow rate of oil into
the hydraulic circuits to improve torque converter clutch apply and
release functions and to reduce heat buildup in the transmission to
prevent torque converter damage or burn out.
2. Brief Description of the Prior Art
The majority of automatic transmission pressure regulation systems
presently in use operate on a pulsed delivery principle. This
pulsed delivery is the result of the valve's mechanical properties.
Conventional valves are produced on automatic lathes and are round
when viewed from an end view. Such valves have a plurality of
outwardly extending lands which function to block or establish oil
flow to or from lube circuits and components of the transmission
such as the torque converter and lubrication and relief valve
circuits. Conventional lands when viewed from the side appear to
have squared 90.degree. corners in that the front, rear and outer
faces thereof and thus are planar along any given line. Although
forming the lands with flat faces is easy and economical, in
operation, the valves must cycle IN and OUT, opening and closing
their respective flow ports to regulate oil flow thus creating a
hydraulic pulse during each cycle. In essence, there is an instant
charge or pulse of oil being sent to the torque convert and the
lubrication relief valve circuits as the lands move to open flow to
the inlet ports thereto.
In addition, automatic transmissions do not have perfectly sealed
hydraulic circuits, and some leakage occurs, such in clutch drum
apply circuits, accumulators, servos, at valves and plugs in the
valve body, or loss of output efficiency in the transmission pump
assembly due to internal "backwash". Further, leakage increases as
oil is heated and becomes less viscous.
By way of example, if, as in the Honda 4 & 5 speed automatic, a
transmission pump is not designed with sufficient output capacity,
system wide pressure will fall below the minimum requirements and
begin to shut down secondary systems, like torque converter fill
and flow to the transmission cooler.
The pressure regular valve springs in the Honda 4 and 5 speed
transmissions are calibrated to regulate system pressure to a
minimum of approximately 118 psi, and a maximum of approximately
210 psi, depending on operating conditions. Although the pressure
regulator may be able to sustain the pressure within the circuits
while the fluid is cooler and thicker, under hotter operating
conditions, and when the vehicle is at a stop and transmission is
in a drive gear at idle, the pump will not be able to produce
enough gallons per minute (GPM) to overcome all the accumulated
leaks and maintain pressure sufficient to hold the pressure
regulator valve open against valve springs. Main line pressure then
drops well below the minimum desired 118 psi. It is typical to see
HOT pressure readings of 90 psi at idle, and VERY HOT readings as
low as 60 psi. But any time the pressure falls below 118 psi, the
pressure regulator valve closes, shutting off fluid flow to
converter, cooler, and lubrication circuits. At this point the
pressure regulator valve is not functioning and there is
insufficient fluid being supplied to the torque converter. When at
a stop, if there is not sufficient flow to hold the converter
clutch released, it will drag and burn out the clutch lining (a
layer of friction material bonded to the damper assembly). If the
pressure regulator closes while the control system has the
converter clutch in APPLY mode, there will be insufficient pressure
to keep it firmly applied, and slippage occurs. This slippage also
results in clutch lining burnout.
In view of the foregoing, there is a need to improve the operating
characteristics of the pressure regulator control valve used on
some conventional automotive transmissions in order to avoid the
problems associated with pulsed oil supply and insufficient volume
flow to the torque converter and lube circuits, and to improve
supply of oil from the transmission pump to the torque converter to
prevent overheating and damage.
SUMMARY OF THE INVENTION
The present invention is directed to a new pressure regulator valve
for use in automotive automatic transmissions to control
transmission fluid flow between a transmission pump and to a torque
converter, cooler and lubrication circuits of the transmission and
is particularly adapted for use in certain Honda 4 and 5 speed
automatic transmissions. The valve is formed having a valve core
portion having three spaced lands extending outwardly there from
for controlling fluid flow from the pump to the torque converter,
lube and relief valve circuit and a pressure regulator balance
port. The valve is configured to be installed to replace an
original equipment regulator control valve of the transmission and
thus to reciprocally fit within an existing bore of the
transmission. Unlike the conventional pressure regulator valves
having first, second and third flow port control lands having
substantially flat front and rear faces, the new valves include
second and third lands having inwardly tapering conical rear faces
that extend toward the first or rear balance control land of the
valve, preferably at an angle of between 25.degree. to 50.degree.,
relative to the core of the valve. In some embodiments the rear
tapering faces are smooth conical surfaces and in others the rear
tapering faces may be stepped conical structures.
In a first embodiment of the regulator control valve of the
invention, the tapered rear surfaces of the second and third lands
are both generally angled at approximately 35.degree. while the
first balance land has flat front and rear faces similar to the
first land of the original equipment valve. In a second embodiment
of the invention, the regulator control valve includes second and
third lands which taper at different angles relative to the core of
the valve. In the embodiment shown herein, the second land tapering
surface extends at an angle of approximately 35.degree. relative to
the core whereas the angle of the rear surface of the third land
extends at approximately 45.degree. relative to the core. In the
second embodiment, the first land includes a front conical face
which tapers inwardly toward the core and the intermediate or
second land has a front face having conical outer edge portion
angled at approximately 45.degree.. Also, in the second embodiment,
a pair of metering flats may be provided along the outer edge of
the rear face of the first land with the flats being spaced
180.degree. from one another.
Due to the sloped rear faces of the second and third lands of the
pressure regulator valve of the present invention, as the lands
move relative to the fluid inlets or outlets in the surrounding
transmission circuits, a steady fluid stream is provided at
progressively changing rates. Because of this, the valve functions
to dynamically regulate flow at any point along the sloped or
tapered surfaces without fully closing or opening. The regulation
point along the sloped surfaces of the lands is determined
according to available volume supply from the transmission pump and
is therefore dynamically sensitive to temperature and fluid
viscosity as well as engine RPM and transmission pump speed and
output.
With either of the embodiments of the invention, an additional
balance assist is provided by a spring which seats within a blind
hole made in the inner end of the pressure regulator valve and
which extends along a central axis of the core of the valve. The
balance spring is provided for creating additional fluid feed
through the valve at pressures below the normal opening pressure
for feed to the torque converter. It has been determined that while
operating some Honda.RTM. vehicles in third gear at speeds of about
30 to 35 miles per hour with lockup command ON and with the engine
operation at about 1200 RPM, the transmission becomes hot and
pressures against the valve falls below normal opening pressure for
moving the intermediate or second land to establish flow to the
torque converter. The spring is partially seated within the blind
hole. The additional spring provides approximately 5.5 pounds of
tension when the valve is bottomed at rest within the valve bore of
the transmission. When the valve is regulating on the pressure
regulator dump land number three, the additional spring is not
functional. The additional spring only comes into play at lower RPM
when the pressure regulator valve begins to close the torque
converter feed circuit when pressures drop below 118 psi, for the
Honda.RTM. transmissions described herein, and retains the valve in
position to permit oil to flow to the torque converter until the
line pressure drops to between approximately 90 to 95 psi. The
balance assist spring thus extends the functional range of oil feed
to the torque converter so that it will have sufficient oil for
safe lockup when in third gear.
The invention further provides for increasing leakage flow to the
torque converter by reducing the diameter of the second or
intermediate land of the valve from the original equipment
specifications. By way of example, for the Honda.RTM. 4 and 5 speed
automatic transmissions, the diameter of the center or number two
land which is normally 0.511 to 0.5112 inch, the same for all three
lands, is reduced to approximately 0.5093 inch, plus or minus
0.0002 inch. The increase created in bore clearance supplies a full
time torque converter feed equivalent to a hole of approximately
0.55 to 0.059 inch diameter. This additional feed will ensure that
sufficient pressure is applied to hold a damper plate released when
the transmission is operating in drive and rear engagements and
when the vehicle is stopped and in drive. This prevents severe
clutch heat buildup.
BRIEF DESCRIPTION OF THE DRAWINGS
The invention will be better understood with reference to the
attached drawings wherein:
FIG. 1 is a cut away view of a portion of a Honda.RTM. transmission
showing a pressure regulator dump, transmission pump input, torque
converter output and pressure regulator balance;
FIG. 2 is a cross section taken along line 2-2 of FIG. 1 showing an
original equipment pressure regulator valve positioned at rest
within a bore of the transmission;
FIG. 3 is view similar to FIG. 2 showing a boost sleeve and springs
mounted over the free elongated end of the valve also shown in FIG.
2;
FIG. 4 is a cross sectional illustration view of the pressure
regulator valve and boost sleeve of FIG. 3 and showing portions of
the lubrication flow paths relative to the valve;
FIG. 5 is a side view of a first embodiment of pressure regulator
valve in accordance with the teachings of the present
invention;
FIG. 6 is a side view of a second embodiment of pressure regulator
valve in accordance with the teachings of the invention;
FIG. 7 is a side view of the pressure regulator valve of FIG. 5
shown in an at rest position within the bore of the transmission
shown in FIG. 2;
FIG. 8 is a view similar to FIG. 7 showing the valve approaching
maximum flow to the torque converter;
FIG. 9 is a side perspective assembly view of a varied embodiment
of pressure regulator control valve in accordance with the present
invention;
FIG. 10 is a view similar to FIG. 9 showing a biasing spring
mounted within the inner end of the valve shown in FIG. 9;
FIG. 11 is a view of the valve shown in FIGS. 9 and 10 positioned
within the transmission bore of FIG. 2; and
FIG. 12 is partial illustration view of one of the lands of the
valve shown in FIG. 5 having a varied stepped tapering
structure.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
With continued reference to the drawings, a convention Honda.RTM.
pressure regulator casing 9 is shown in FIG. 1 wherein openings to
the pressure regulator dump 10, the pump volume output line 11,
torque converter feed 12 and pressure regulator balance 13 are
shown. In FIG. 2 which is a cross section through FIG. 1, an
original equipment pressure regulator valve 15 is shown within a
bore 16. The valve includes a reduced diameter core 17 and three
outwardly extending lands including a first inner pressure
regulator balance land 18, a second intermediate converter feed
control land 19 and an outer regulation line dump land 20. As shown
in FIG. 3, a pair of small metering flats 22 are made in both the
outer and rear faces of lands 19 and 20 and on opposite sides of
the lands such that there are two metering flats on each of these
lands spaced at 180.degree. from one another.
As shown in FIGS. 2 and 3, the front and rear faces of each land
are generally flat such that when the valve is viewed from the side
as shown in the two figures, the upper and lower corners of each
land are squared forming 90.degree. corners. Due to the
configuration of the lands, as the valve 15 moves the lands to
initially open to the pressure release balance line 13, the torque
converter feed 12 or the pressure regulator dump line 10 to a
pressure relief valve, there is an instance pulse flow created to
the outputs.
With reference to FIGS. 3 and 4, a boost sleeve assembly 23 is
shown for maintaining the pressure regulator valve 15 in a rest
state wherein fluid from a transmission pump 24 is not supplied to
a torque converter 25. The boost sleeve assembly includes a sleeve
27 with enlarged head 28 which is engaged by a stator arm, not
shown. Mounted about an extension 30 of the valve 15 are a primary
outer pressure regulator spring 32 and a secondary inner pressure
regulator boost spring 34. Generally the secondary boost spring 34
does not exert force against the pressure regulator valve 15 when
the stator arm exerts no force against the head of the boost
sleeve. When idling in neutral, the pressure regulated is
determined only by the tension of the primary pressure regulator
spring 32. In Honda.RTM. 4 and 5 speed automatic transmissions,
approximately 118 psi is required to open the pressure regulator
valve against the springs to begin feeding fluid to the torque
converter 25. Below 118 psi, the pressure regulator valve remains
closed. Generally, when idling in neutral or drive at cold start,
approximately 120 psi is developed against the valve. As the fluid
within the transmission becomes heated and the viscosity of the
fluid thins, the pressures against the valve normally fall to as
low as 50 to 60 psi such that the pressure regulator valve is not
opened and no fluid is supplied to the torque converter except
fluid that leaks within the transmission. The metering flats 22 are
provided in order to permit some minimal flow by the intermediate
or second land 19 before pressure within the lubrication circuits
from the transmission pump rise to a level to force the pressure
regulator valve to open to the torque converter. From measurements
taken, it is estimated that only 0.1 to 0.7 gallons per minute
(GPM) of transmission fluid are supplied to the torque convert when
the transmission fluid is extremely hot and the pressure within the
transmission is below the level of 118 psi. The flow level may
increase to 1.2 GPM when the valve land 19 "cracks" open the feed
port 12 to the torque converter circuit.
In order to overcome the overheating and low fluid flow problems of
the original operating pressure regulator valve 15, the present
invention includes a first embodiment of pressure regulator valve
40 having generally the same length and diameter dimensions and
land widths as the original equipment valve 15 except that rear
portions 41 and 42 of the second and third lands, 43 and 44,
respectively, are tapered toward the core portions 45 and 46,
respectively, and the inner land 47 of the valve is not tapered
toward core portion 48, as is shown in FIG. 5. As the valve 40 is
circular in cross section, the tapered portions are conical in
configuration. In preferred embodiments of the invention, the walls
of the tapered or sloping portions of the lands are smooth
surfaces, however, as shown in FIG. 12, the rear portions 41 and 42
of the lands 43 and 44 may include a series of rearward extending
stepped down portions of progressively reduced diameter as opposed
to the smooth tapered walls of the embodiment of FIG. 5. FIG. 12
shows a modified land 43' with a plurality of stepped down portions
49. Also, the valve 40 includes a through hole 70 in core portion
for passage of balance oil.
As shown in FIG. 5, a preferred angle of taper of the portions 41
and 42 is approximately 35.degree., although this angle may be
varied. What is critical is that the lands to the pressure
regulator dump line 10 and the torque converter feed 12 causes a
variation in flow to be established as the lands 43 and 44 begin to
open or close relative to the ports to the respective fluid
circuits. The inner land 47 of the pressure regulator valve 40 is
configured as a conventional "squared" land. The valve also
includes a frontal extension 50 having annular flanged seat
portions 51 and 52 for the ends of the conventional primary and
secondary pressure regulator springs. The boost sleeve and the
primary and secondary springs described with respect to the
originally operating valve 15 are the same for use with the valve
40 of the invention. The general dimensions of a valve 40 for use
in Honda 4 and 5 speed automatic transmissions are shown in FIG. 5.
It should be noted, however, that the tapered lands taught with the
present invention may be provided on lands of pressure regulator
valves of other models of automatic transmissions taking in mind
that the dimensions of the valve and lands must be changed to be
compatible with such other transmissions.
As shown in FIG. 5, the core portion 46 between the second and
first lands is slightly larger in diameter than the core portion 45
between the second and third lands. Also, in preferred embodiments
of the invention, a hollow blind hole 55 is provided in the core
portions 48 and land 47 which is aligned with a central axis A-A of
the valve 40. The blind hole is provided to receive a supplemental
converter open extension spring 56 for purposes which will be
further described hereinafter.
As previously described, the sloped rear faces 41 and 42 of the
intermediate and third lands 43 and 44, respectively, of the
pressure regulator valve 40 are provided such that as the lands
move relative to the fluid inlets into the torque converter and
pressure regulator dump circuits, respectively, a steady fluid
stream of lubrication and cooling fluid will be provided at
progressively changing rates. Because of this, the valve functions
to dynamically regulate flow at any point along the sloped or
tapered surfaces without fully closing or opening. The regulation
point along the sloped surface of the lands is determined according
to available volume of fluid supply and is therefore dynamically
sensitive to temperature and fluid viscosity as well as engine RPM
and transmission pump speed and output. Due to the flow
characteristics developed with the tapered land configuration, the
pressure regular valve 40 of the inventions will operate more
smoothly to provide a better and more consistent flow of
transmission fluid to the torque converter so as to minimize
converter overheating and burn out which is occurring with the
original equipment operating valves 15.
With specific reference to FIG. 7, the valve 40 is shown fully at
rest within the bore 16 of the transmission. In this position the
land 47 blocks the pressure regulator balance inlet 13 while land
43 blocks the feed to the torque converter circuit and land 44
blocks the pressure regulator dump circuit inlet. When pressure
from the transmission pump is sufficient to move valve 40 against
the primary outer and secondary boost springs 32 and 34, the valve
is shifted to the left within the bore, as shown in FIG. 8, so that
the feed to the torque converter outlet at 12 is almost at full or
maximum flow as the land 43 no longer blocks the outlet and the
land 44 to the pressure regulator dump circuit is just about to
open as the tapered surface 42 thereof is approaching an alignment
to opening to the circuit. In the position shown, balance fluid
enters the valve as the inlet 13 is no longer blocked by land
47.
With specific reference to FIG. 6, a second embodiment of pressure
regulator valve 140 is shown. The numbers used to describe the
second embodiment will generally be the same numbers as used to
describe the first embodiment raised by 100. The pressure regulator
valve 140 is also generally the same length and diameter dimensions
and has the same land widths as the original equipment valve 15
except that rear portions 141 and 142 of the second torque
converter feed and third regulation dump lands, 143 and 144,
respectively, are tapered toward the core portions 145 and 146,
respectively, and the inner balance land 147 of the valve is also
slightly tapered toward core portion 148, as is shown in FIG. 6. As
the valve 140 is circular in cross section, the tapered portions
are conical in configuration. In preferred embodiments of the
invention, the walls of the tapered or sloping portions of the
lands are smooth surfaces, however, as shown in FIG. 12, the rear
portions of the lands 143 and 144 may include a series of rearward
extending stepped down portions 49 of progressively reduced
diameter as opposed to the smooth tapered walls of the embodiment
of FIG. 6.
As shown in FIG. 6, a preferred angle of taper of the portions 141
is approximately 35.degree. while a preferred angle of taper of
portion 142 is shown at 45.degree., although these angles may be
varied. What is critical is that the lands to the pressure
regulator dump line 10 and the torque converter feed 12 causes a
variation in flow to be established as the lands 143 and 144 begin
to open or close relative to the ports to the respective fluid
circuits. The inner land 147 of the pressure regulator valve 140 is
configured so as to also have a tapered front wall 149 which is
conical and angled at approximately 45.degree. toward the core 145.
Also, the torque converter feed control land 143 may also have a
tapered front face 156 of a conical shape as shown at an angle of
approximately 45.degree., however, these angles may vary as set
forth above with respect to the first embodiment of the invention.
The pressure regulator valve 140 also includes a frontal extension
150 having annular flanged seat portions 151 and 152 for the ends
of the conventional primary and secondary pressure regulator
springs. The boost sleeve and the primary and secondary springs
described with respect to the originally operating valve 15 are the
same for use with the valve 140 of the invention. The general
dimensions of a valve 140 for use in Honda 4 and 5 speed automatic
transmissions are shown in FIG. 6.
As also shown in FIG. 6, the core portion 146 between the second
and first lands is slightly larger in diameter than the core
portion 145 between the second and third lands and includes a
through hole 170 for passage of balance oil. Also, as with the
first embodiment of the invention, a hollow blind hole 155 is
provided in the core portions 148 and land 147 which is aligned
with a central axis A-A of the valve 140. The blind hole is
provided to receive a supplemental converter open extension spring
56 for purposes which will be further described hereinafter. The
second embodiment of valve 140 may also be provided with a pair of
metering flats 152 which are provided on an outer edge of the rear
face of the land 147 and which function as described with respect
to the conventional metering flats provided on the valve 15.
The pressure regulator valves 40 and 140 of the present invention
are able to fine tune fluid flow through the transmission to the
torque converter while minimizing waste flow of conventional pulse
type valves 15 of the conventional Honda.RTM. design. Further, the
valves 40 and 140 drastically reduce pressure oscillation and valve
bore wear. The valves 40 and 140 displace fluid flow to compensate
for insufficient volume of fluid flow from under capacity
transmission pumps especially at low engine RPM and thus correct
the most serious malfunctions in original operating transmissions
of torque converter lockup clutch failure.
With specific reference to FIGS. 9-11, in order to correct the lack
of proper fluid supply to the torque converter at various operating
engine speeds and transmission settings, such as at low engine RPMs
and when the transmission fluid is hot and the pressure within the
transmission lubrication or hydraulic circuits is below the
pressure to effectively open the pressure regulator valve 40 to
properly supply fluid to the torque converter, a balance assist or
converter open extension spring 56 is mounted within the blind hole
55 of the valve 40 or blind hole 155 of valve 140. The spring is
designed to be effective at low RPM such that when the pressure
regulator valve 40, 140 begins to close flow to the torque
converter circuit 11, the spring will provide additional force to
maintain the valve open even though pressures within the circuits
fall below the normal closing pressure established by the valve
springs of approximately 118 psi. The spring 56 provides
approximately 5.5 pounds of tension when the valve is bottomed in
the valve bore as shown in FIG. 10. The force is sufficient to
maintain the valve 40 slightly opened to the converter feed circuit
until the line pressures fall to 90 to 95 psi. The spring thus
extends flow to the torque converter so as to maintain pressure on
a damper plate of the converter to keep it applied by oil from the
turbine side of the converter at lower operating pressures so as to
prevent overheating and damage to the to the converter by converter
lockup clutch burn out or failure.
Also, in accordance with the invention, in the preferred
embodiments, in order to provide sufficient fluid flow to the
torque converter to prevent dragging of the clutch lining and sever
heat buildup within the converter, the diameter of the converter
feed land 43, 143 is reduced to create additional leakage between
the valve 40, 140 and the bore 16 of the transmission. The factory
diameter of the three lands of the Honda.RTM. 4 and 5 speed
automatic transmissions is set at 0.511 to 0.5112 inch. In keeping
with the present invention, this dimension of the land 43, 143 is
reduced such as to between 0.5093, plus or minus 0.0002 inch. In
this manner, a full time or continuous feed of transmission fluid
flows from the transmission pump to the torque converter. The
clearance is equal to a hole of 0.55 to 0.59 inch and permits more
cooling flow to reduce the occurrence of converter over heating at
low engine RPMs.
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